JPS62228845A - Heat pump device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention uses a non-azeotropic mixed refrigerant in a heat pump device, particularly in a heating and cooling device, and constantly adapts to the load by varying the concentration of the refrigerant flowing through the main circuit. The present invention relates to a heat pump device that generates heating and cooling capacity.

Conventional technology Conventionally, as a method of varying the capacity of a heat pump device, a non-azeotropic mixed refrigerant is used as the refrigerant, and a separator separates the refrigerant into a high boiling point refrigerant and a low boiling point refrigerant, thereby changing the refrigerant composition in the main circuit. A system with variable capacity has been proposed, in which the composition of the refrigerant is changed to change its suction specific volume and the amount of circulation, and it is also possible to add such a separation method to the system of changing the compressor rotation speed. A method using rectification has been proposed as a separation method.

Our prior invention is as shown in FIG. 2. In Fig. 2, 1 is a compressor, 2 is a four-way valve, 3 is a load side heat exchanger, 4 is a main throttling device, 6 is a heat source side heat exchanger, 7 is a separator, 8 is a top cooling heat exchanger, Reference numeral 9 denotes a bottom heating heat exchanger. During heating, refrigerant is supplied from the load-side heat exchanger 3, which serves as a condenser, to the separator 7 in parallel with the main circuit, and in the separator 7, the refrigerant is sealed into the cycle by a rectification method. The resulting non-azeotropic mixed refrigerant is separated into high-boiling point components and low-boiling point components, and the high-boiling point component refrigerant or low-boiling point component refrigerant is injected into the main cycle from the reservoir 10.11 at the bottom or top of the tower. Capacity is controlled by changing the refrigerant composition of the cycle, and at this time, in order to perform rectification separation during both heating and cooling, the bottom heating heat exchanger 9 is operated by compressor 1 and four-way valve 2. The discharge gas between the four-way valve 2 and the accumulator 12 is used as a heating source, and the suction gas between the four-way valve 2 and the accumulator 12 is used as a cooling source in the tower top cooling heat exchanger 8. With this configuration, even if the flow direction of the refrigerant in the main cycle is reversed during cooling and heating, the necessary heating and cooling for rectification separation can be achieved.

Problems to be Solved by the Invention In the heat pump device of the prior invention described above, it is basically possible to control the composition of the refrigerant, and it is suitable when this is necessary for both cooling and heating.

However, when actually using such a compositional separation cycle to control the joint capacity during cooling and heating, during heating the low boiling point components are generally increased in the main cycle to gain capacity, and conversely during cooling the low boiling point components are increased. Since high pressure increases at +7 nochi, it may be desirable to operate the raw cycle rich in high-boiling components to increase efficiency. During heating, it is desirable to operate the refrigerant with a composition rich in low boiling points, and to operate with the same composition as the enclosed refrigerant, which is rich in low boiling points, without performing rectification separation.

In addition, according to the configuration of the prior invention, heating and cooling for rectification separation are active during both cooling and heating, regardless of whether or not the concentration is varied in the main cycle. When cooling, the temperature at the condenser inlet drops, which causes a loss of capacity, especially at the start of heating. Furthermore, since the overhead cooling heat exchanger uses suction gas, the heat transfer coefficient is low and the heat exchanger becomes large.

Therefore, in the present invention, there is no rectification separation during heating, high efficiency operation is achieved by rectification separation during cooling, and furthermore, during heating,
The aim is to obtain a heat pump device that increases the efficiency of the heat exchanger, and also to reduce the size of the tower top heat exchanger.

Means for solving the problem Separation is performed using an introduction section that connects the bottom of the separator and the condenser outlet for heating/cooling, and an outlet that connects the bottom of the separator and the inlet of the evaporator for heating/cooling. The refrigerant piping between the four-way valve and the heat exchanger on the heat source side is located at the bottom of the separator column as a heating source, and the refrigerant piping between the expansion device and the load side heat exchanger is placed at the top of the separator tower. It is configured to be positioned as a cooling source.

According to the present invention configured as described above, the separator is connected to the main cycle in a low boiling point storage system, and during cooling, high-temperature refrigerant flows between the four-way valve and the heat source side heat exchanger, so the bottom of the separator column is heated. Between the throttle device and the load-side heat exchanger, the refrigerant becomes a low-temperature refrigerant and can cool the top of the separator tower. As a result, rectification separation is performed during cooling, and since it is a low boiling point storage method, the main cycle can have a refrigerant composition rich in high boiling points. On the other hand, during heating, there is no heating or cooling effect that activates rectification in the separator, so no rectification separation occurs, and operation can be performed with a refrigerant composition rich in low boiling points of the enclosed refrigerant composition, and there is no heating or cooling for rectification separation. This allows operation without heat loss.

Embodiment A first example in which the heat pump device according to the present invention is applied to an air-conditioning device.
This will be explained below using figures.

In the figure, 1 to 4 and 6 are the same components as in the previous invention, and a separator 13 is connected between the load side heat exchanger 3 and the expansion device 4.
piping 14 connected to , the expansion device 4 and the heat source side heat exchanger 6
During main cycle operation, the refrigerant mainly passes through the throttling device 4 and the above-mentioned pipes 14 and 16 and then via the separator 13. It is divided into a main cycle and a parallel cycle. At this time, a piping 16 is provided at the upper part of the separator 13 so that the separator 1
3 is cooled and liquefied at the top heat exchanger 17, stored in a reservoir 18, and a reservoir piping 19 is provided for refluxing the liquid from the reservoir 18 to the top of the tower.

At this time, the refrigerant introduced to the tower top cooler 17 is the refrigerant between the load-side heat exchanger 3 and the expansion device 4t, and the piping 16
The refrigerant guided to the bottom heat exchanger 20 that heats the refrigerant passing through is configured to be the refrigerant between the heat source side heat exchanger e and the four-way valve 2. Furthermore, the piping 14.15 has a restriction 21.2.
Check valves 23, 24 are provided in parallel with 2. In the heat pump device having such a configuration, the operation during cooling and heating will be explained.

First, during heating, the refrigerant flows as shown by the solid line in the figure, and the refrigerant enters the separator 13 through the piping 14 as a liquid refrigerant, and since no gas is generated in the separator 13, the rectification effect is effective. Instead, the refrigerant composition of the main cycle remains the same as the refrigerant composition rich in low boiling points at the time of sealing, allowing operation to maintain high heating capacity. At this time, in the top heat exchanger 17, the separator 1
Since the temperature is almost the same as that of the refrigerant in the column 3, it does not act as a heat exchanger, but in the bottom heat exchanger 2o, the liquid refrigerant flowing out through the separator 13 and the υ pipe 15 is cooled. In this way, the rectifying action can be completely stopped during heating, and there is no heat loss due to heating the refrigerant on the separator 13 side, allowing highly efficient operation. Furthermore, the liquid refrigerant flowing out of the separator 13 is further supercooled by the low temperature refrigerant exiting the heat source side heat exchanger θ, increasing the refrigerating capacity and enabling highly efficient operation.

Next, the operation during cooling operation will be explained. During cooling, the refrigerant flows as shown by the broken line in the figure, and the liquid refrigerant that enters the separator 13 from the pipe 15 is exchanged with the high temperature gas refrigerant in the bottom heat exchanger 20. is heated to generate gas components, which flow into the separator 13. The gas component that has flowed into the separator 13 rises inside the separator 13, passes through the pipe 16, is cooled with a low-d refrigerant in the top heat exchanger 1γ, and is liquefied. The liquid is refluxed to the top, and this liquid and the rising gas come into gas-liquid contact in the separator 13 to perform a rectifying action, and a low-boiling point refrigerant is stored in the reservoir 18, and the main cycle is rich in high-boiling point refrigerant. It has a cycle composition, which eliminates the high pressure rise that occurs when operating with a low boiling point refrigerant during cooling, and allows operation with high efficiency.

At this time, the load side heat exchanger 3 is used as a cooling source from the expansion device 4.
Since a gas-liquid two-phase refrigerant is used in between, a high heat transfer coefficient can be obtained, and therefore the top heat exchanger 17 can be configured compactly.

In addition, for example, during cooling, by providing a throttle in the piping 15 that serves as the introduction part to the separator 13 to generate and introduce gas components into the separator 13 at an intermediate pressure, the bottom heat exchanger 2
It is also possible to reduce the amount of heating at zero and reduce the heat loss that occurs during separation. Basically, separation is not applied during heating, but as a method of using both separation during cooling and cases where separation is not applied, it is possible to stop heating by using a bypass, or to reduce the amount of refrigerant flowing into the separator 13. This is possible by increasing the amount of refrigerant, or by returning the refrigerant from the reservoir 18 to the low-pressure piping. In this embodiment, the bottom heat exchanger 20 is connected to the pipe 1
5, but it may be attached to the pipe 14, or may be configured to span both pipes.

As described in detail, in the heat pump device of the present invention, a non-azeotropic mixed refrigerant is operated with a refrigerant composition suitable for cooling and heating, and is operated with a refrigerant composition rich in high boiling point components during cooling. During heating, the refrigerant is operated with a refrigerant composition rich in low-boiling components, which is the same as the sealed composition, to achieve high performance.At this time, the heating source for rectification separation during cooling is As a cooling source, a high-temperature refrigerant is used between the heat exchanger on the heat source side and the four-way valve, and a low-temperature refrigerant between the heat exchanger on the load side is used as a cooling source, rather than a throttling device, so during heating, this heating source becomes a supercooling source. The refrigerant in the cooling source during cooling separation is in a gas-liquid two-phase state, so it can be made compact as a heat exchanger.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram of a heat pump device according to an embodiment of the present invention, and FIG. 2 is a cycle configuration diagram showing an embodiment of a prior invention related to the present invention. 1... Compressor, 3... Load side heat exchanger, 2... Four-way valve, 4... Throttle device, 6
... Heat source side heat exchanger, 13 ... Separator, 17 ... Tower top heat exchanger, 20 ... Tower bottom heat exchanger.

Claims (2)

[Claims] (1) A main cycle is constructed by enclosing a non-azeotropic mixed refrigerant and connecting a compressor, a four-way valve, a load-side heat exchanger, a throttling device, and a heat source-side heat exchanger in an annular manner. A separator that separates the azeotropic mixed refrigerant, a pipe that connects the separator, the heat source side heat exchanger, and the throttling device, and a connection between the bottom of the separator and the load side heat exchanger. It has piping to
Piping from the throttle device to the load-side heat exchanger is attached to the top of the separator, and piping from the four-way valve to the heat source-side heat exchanger is attached to the bottom of the separator. heat pump equipment. (2) The heat pump device according to claim 1, characterized in that the separator has an intermediate pressure.